Turbo-compressor-condenser-expander

ABSTRACT

An isothermal turbo-compressor-condenser-expander arrangement includes heat-transferring blades that are mounted on, or surround, individual conduits. In operation, the open framework rotates in free air to promote heat exchange. The assembly includes a first plurality of spokes extending radially outwardly from a first central hub to an outer perimeter with first radial conduits that transport refrigerant under centrifugal force and compression from the hub to the outer perimeter. The first radial conduits include heat exchanging blades. A second plurality of spokes extend radially outwardly from a second central hub that each includes a second thermally-insulated conduit that transports refrigerant from the outer perimeter to the second central hub. Axial conduits extend axially at the outer perimeter. At least some of the axial conduits include an axial blade in thermal communication with the conduit.

RELATED APPLICATIONS

This application is a divisional of co-pending U.S. patent applicationSer. No. 12/691,383, filed Jan. 21, 2010, entitledTURBO-COMPRESSOR-CONDENSER-EXPANDER, the entire disclosure of which isherein incorporated by reference, which claims the benefit of U.S.Provisional Patent Application Ser. No. 61/146,022, filed Jan. 21, 2009,entitled ISOTHERMAL TURBOCOMPRESSOR, the entire disclosure of which isalso herein incorporated by reference.

FIELD OF THE INVENTION

The present invention relates generally to the field of devices used forthe compression and condensation of refrigerant in an air-conditioning,refrigeration, heat-pumping, or other cooling/heat-transfer system.

BACKGROUND OF THE INVENTION

In air-conditioning, refrigeration, heat-pumping, and otherrefrigerant-based systems, heat is removed from a colder side of adevice or system and transferred to a warmer side. For example in thecase of air-conditioning, heat is transferred from the interior of abuilding, vehicle or other enclosed space to the exterior atmosphere. Astandard process of removing colder air from one chamber andtransferring it to another chamber or area includes four steps:compression of a refrigerant, followed by heat expulsion to the warmside, followed by a sudden expansion or other means of decompression,and finally absorption of heat from the cold side.

According to a typical prior art system, such as that illustrated inFIG. 1, both a compressor and a heat exchanger are separately requiredto accomplish the first two steps of the refrigeration cycle. Asillustrated, the prior art air-conditioning/cooling system 100 definedby a refrigerant loop includes a compressor 110 that compresses therefrigerant fluid (typically a gas at that stage) by pressurizing it,which causes its temperature to increase in the output, compressedrefrigerant. An electrical (or other power source) drive typicallydelivers the mechanical energy required to perform the compression ofthe refrigerant. The compressor typically uses an impeller or piston orother arrangement to compress the refrigerant. As shown, the refrigerantflows through the system loop 100 in accordance with the flow arrows121.

The system 100 also includes a condenser 120, comprising an exteriorcoil 122, that provides a surface area capable of sufficient heatexchange as the heat generated by the (heated) pressurized refrigerantwithin the coil is transferred to the exterior (cooler side) by theatmospheric air (or other transfer fluid) passing over the coil. Thiscauses the refrigerant to expel heat and liquefy. Once a sufficientamount of heat is removed, the refrigerant is expanded and decompressedin an expansion valve 125, causing its temperature to drop to atemperature below that of the cold chamber. The refrigerant subsequentlyenters a heat exchanger 132, where it flows trough a set of coils 131and is exposed (typically by means of a fan 140) to the air of the coldchamber, from which, by virtue of the refrigerant's lower temperature,heat is extracted and communicated to the refrigerant, which vaporizesin the process (i.e. the refrigerant “absorbs” the heat).

As the refrigerant passes through the heat exchanger 132 (consisting ofcoil 131 and fan 140) inside the chamber 130 and becomes warmer, heat istransferred from the surrounding space 132 by a fan 140 (oralternatively ram air, as in the case of vehicle motion), and producescool air that is ejected into the space being the object of cooling. Therefrigerant returns to a vapor phase based upon the heat withdrawn fromthe air that passed over the coil 131. The refrigerant vapor thenreturns to the compressor 110 to become a high-pressure gas again. Theheat then flows from the high-temperature gas to the lower-temperatureair of the space surrounding the coil 122. This heat loss causes thehigh-pressure gas to condense to liquid, which again passes throughexpansion valve 125 into coil 131 inside the chamber 130 to repeat thecompression, and then condensation cycles. This process is continuallyperformed to condition air in compartments (i.e. cool or heat) asdesired.

A disadvantage of the air-conditioning arrangement illustrated in FIG. 1is that it requires a compressor to first pressurize the refrigerant sothat it becomes high-pressure, heated gas, a condenser for providing theheat exchange required to cool down the refrigerant before it passesinto the coil within the refrigerant compartment, and an expansionvalve. This typically requires three separate and discrete devices, onefor performing each process within the air-conditioning/refrigerationcycle and interconnected by appropriate tubing. This reduces efficiencyand increases component count and cost. More particularly, it is awell-established fact of thermodynamics that, at identical pressures,more energy is required to compress a gas at a higher temperature thanthe same gas at a lower temperature. Thus, compression with delay ofheat expulsion until completion of the compression requires more energythan compression with anticipated heat expulsion during the compression.The ability to carry out this process in a more-isothermal manner, inwhich heat is removed from the refrigerant simultaneously with thecompression, can provide a more-efficient overall process. Anotherdisadvantage is the physical separation of the expansion valve 125 fromthe compressor 110, which prevents transfer of energy removed from thefluid during expansion to the compressor in order to reduce its energydemand.

Various systems have attempted to overcome this disadvantage, includingproviding systems having multi-stage compression components separated byintermediate cooling stages, on one hand, and systems with expansionthrough a turbine sharing a rotating shaft with the compressor, on theother hand. However, these systems typically require an increased numberof components relative to a conventional arrangement, for example afirst-stage compressor, flash chamber, heat exchanger, and second-stagecompressor. These multi-stage systems have typically been limited tolarge-scale refrigeration systems due to the number of components (andassociated higher cost) required for operation. This cost and complexityrenders such systems, undesirable for smaller scale air-conditioning andrefrigeration applications.

According to prior art arrangements, piston-type compressors areprovided that include cooling jackets that remove heat from thecompressor wall to enhance isothermalism, and/or intermediate heatexchangers between the stages of a multi-stage compressor assembly.However, these compressors operate with a reciprocating piston that doesnot allow sufficient physical proximity between the refrigerant undercompression (inside the piston chamber) and the fluid (such asatmospheric air) used for the cooling, and only a fraction of the heatcan be extracted during the compression. There is currently no availablesystem in which a large portion of cooling (and condensation) occursduring the compression cycle to improve efficiency, particularly, onewhich does not involve a series of separate components that increasecost and complexity.

It is thus desirable to provide a single apparatus capable of performingsimultaneous refrigerant compression, condensation, and expansion,thereby improving efficiency and overall design of air-conditioning,refrigeration and heat-pumping systems. This system should furtherprovide the advantage of a fewer number of components for performing therequired heat transfer from a cold side to a warmer side.

SUMMARY OF THE INVENTION

This invention overcomes disadvantages of the prior art by providing acombined device that incorporates an isothermal turbocompressor, aturbocondenser and turboexpander for use in a system that transfers heatfrom a colder side to a warmer side, for example, a refrigerant-basedheat-pumping system that performs the compression and condensation ofthe refrigerant in an air-conditioning/refrigeration heat-exchangecycle.

In one embodiment, an exemplary isothermal turbocompressor (withoutturbocondenser or turboexpander stages) includes a central hub having aplurality of spokes extending radially outwardly therefrom to an outerstationary plenum. In operation, the rotating central hub directsrefrigerant from an inlet feeding tube, which then flows trough at leastone tube disposed in each of the spokes. The tubes direct the flow ofrefrigerant to the outer stationary plenum, via the centrifugal forceexerted by the spinning of the central hub according to one embodiment.This applied centrifugal force also performs the compression of therefrigerant by the force exerted thereon as it is collected within theplenum.

According to another illustrative embodiment, the flow of refrigerant isdirected outwardly through a spoke framework, and back inwardly toundergo centrifugal force exerted by spinning the central hub. Thisperforms the compression and then condensation required during therefrigeration cycle.

More particularly, the outer plenum includes a circumferential groove orwell that faces openings in the spokes, and from which compressedrefrigerant exits the spokes and enters the plenum. Once in the plenum,the compressed refrigerant is directed to at least one externallydirected outlet. The stationary inlet feeding tube of the hub and theouter plenum are joined to the spinning component by associated seals.

The spokes can define fins having an appropriate aerodynamic shape andconstructed from a material with good heat-transfer characteristics. Thefins generate an airflow over their surface by drawing the coolingfluid, typically air, across the device and thereby cooling therefrigerant within the spokes. The turbocompressor thus also acts as afan, with the spokes of the compressor collectively acting as a fan,thereby cooling and thus condensing the refrigerant simultaneously whileit is compressed. In this manner, a device can perform both thecompression and cooling stages of a refrigerant in an air-conditioningsystem, and thereby provide a more-isothermal compression process asheat is withdrawn from the refrigerant via the thermal exchange betweenthe cooling fluid and the surface of the spokes as the compressionoccurs. The motor that rotationally drives the spokes with respect tothe inlet and plenum can be variable in speed.

In an illustrative embodiment, the isothermal turbocompressor includes acentral hub mounted on a rotating shaft, driven by a motor, to therebycause the central hub to rotate. The central hub having an inner volumereceiving a flow of refrigerant from a rotationally interconnectedstationary inlet. A plurality of spokes are attached to, and eachextends radially outwardly from, the central hub to a rim. The spokeseach define a shape that generates lift during rotation of the hub so asto direct airflow thereover. At least some of the spokes eachrespectively include a conduit that extends from the inner volume of thehub to a radially outward wall of the rim. A plenum is provided with acircumferential annular well in which the rim rotates. The well isconstructed and arranged to collect the refrigerant in a pressurizedstate from each of the conduits, and the plenum includes at least oneoutlet located in fluid communication with the annular well.

According to an illustrative embodiment, the open framework defines acombined turbo-compressor-condenser-expander arrangement, which includesheat-transferring blades that are mounted on, or surround, individualconduits to promote air exchange and heat transfer. In operation, theopen framework rotates in free air to promote heat exchange. Thisoptimizes contact with free air during rotation. The blades are inthermal contact with the conduits in each embodiment.

In an illustrative embodiment an isothermalturbo-compressor-condenser-expander assembly includes a first pluralityof spokes extending radially outwardly from a first central hub to anouter perimeter. At least some of the first plurality of spokes eachincludes a first radial conduit that transports refrigerant from thefirst central hub to the outer perimeter and a radial blade in thermalcommunication with the first radial conduit that promotes heat exchangeradially. There is provided a second plurality of spokes extendingradially outwardly from a second central hub located at an axial spacingfrom the first central hub. At least some of the second plurality ofspokes each includes a second radial conduit that transports refrigerantfrom the outer perimeter to the second central hub. The second pluralityof spokes include, among possibly other materials, some thermallyresistant material to act as a thermal barrier. A plurality of axialconduits extend axially at the outer perimeter between the firstplurality of spokes and the second plurality of spokes, and eachinterconnecting the first radial conduit and the second radial conduit,respectively, to direct refrigerant therebetween. At least some of theplurality of axial conduits each includes an axial blade in thermalcommunication with the axial conduit, which promotes heat exchange. Amotor rotates a central axis (such as a solid or hollow drive/connectingshaft) operatively connected to the first central hub and the secondcentral hub to thereby rotate the first plurality of spokes and thesecond plurality of spokes so that the refrigerant experiencescentrifugal force to perform compression with respect to each firstradial conduit and decompression with respect to each second radialconduit. The refrigerant, likewise, experiences condensation withrespect to each axial conduit.

In an illustrative embodiment, the first central hub includes aprecompression assembly. The precompression assembly can comprise ahousing having a piston assembly in fluid communication with each firstradial conduit. The driven central axis defines a hollow shaft thatdirects the refrigerant from an inlet adjacent the second central hubinto the piston assembly so as to be precompressed by the pistonassembly before entering each first radial conduit. The piston assemblycan be driven, for example, by a separate motor or by a shaft thatremains stationary while the housing rotates. The inlet adjacent to thesecond central is illustratively located on a non-rotating inlet baserotating fluid union. Likewise, the rotating fluid union includes anon-rotating outlet base, axially separated from the inlet base. Theoutlet base is in fluid communication with passages that surround acentral passage in communication with the inlet. The passages are influid communication with each second radial conduit. In this manner, theinlet and outlet are both located on one end of the device. A drivepulley or other member can be mounted on the hollow shaft adjacent tothe fluid union.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention description below refers to the accompanying drawings, ofwhich:

FIG. 1, already described, is a block diagram of an air-conditioningsystem comprising a compressor and a condenser according to a prior artarrangement;

FIG. 2 is a block diagram of an air-conditioning/heat-exchange systemincluding an isothermal compressor according to an illustrativeembodiment;

FIG. 3 is a more detailed perspective view of the isothermal compressoraccording to the illustrative embodiment;

FIG. 4 is a cross-sectional view detailing a central hub of theisothermal compressor according to the illustrative embodiment, as takenalong line 4-4 of FIG. 3;

FIG. 5 is a cross-sectional view detailing a spoke of the isothermalcompressor according to the illustrative embodiment, as taken along line5-5 of FIG. 3;

FIG. 6 is a cross-sectional view detailing a spoke of an isothermalcompressor according to an alternate embodiment including a plurality ofparallel tubes therein;

FIG. 7 is a cross-sectional view detailing the junction between a spokeand a stationary plenum of the isothermal compressor according to theillustrative embodiment;

FIG. 8 is a more-detailed illustration of the cross-sectional view ofFIG. 4, showing exemplary sealing components according to anillustrative embodiment;

FIG. 9 is a more-detailed illustration of the cross-sectional view ofFIG. 7, showing exemplary sealing components according to anillustrative embodiment;

FIG. 10 is a schematic diagram of an illustrative point-to-point fluidcircuit in which the turbocompressor is employed to cool and pressurizea gas;

FIG. 11 is a top perspective view of aturbo-compressor-condenser-expander comprising an open framework and afluid circuit that extends from and returns to a hub according to anillustrative embodiment;

FIG. 12 is a bottom perspective view of theturbo-compressor-condenser-expander according to the illustrativeembodiment;

FIG. 13 is a cross-sectional schematic view of theturbo-compressor-condenser-expander according to the illustrativeembodiment;

FIG. 14 is a block diagram of an air-conditioning/heat-exchange transfersystem including a turbo-compressor-condenser-expander according to anillustrative embodiment;

FIG. 15 is a graphical representation of the temperature versus entropyfor a conventional refrigerant compression and decompression compared tothe isothermal turbocompressor according to the illustrative embodiments

FIG. 16 is a side cross section of an airfoil shape applicable to aheat-transfer blade of the turbo-compressor-condenser-expander inaccordance with embodiments herein;

FIG. 17 is a diagram of an arrangement including aturbo-compressor-condenser-expander according to an alternateembodiment, including a coaxial precompressor and a coaxial fluid unionproviding both a refrigerant inlet and refrigerant outlet;

FIG. 18 is a side cross section of the coaxial fluid union and adjacentmain shaft assembly components taken along line 18-18 of FIG. 17; and

FIG. 19 is a side cross section of the coaxial precompressor taken alongline 19-19 of FIG. 17.

DETAILED DESCRIPTION

In accordance with an illustrative embodiment, there is provided anisothermal turbocompressor (with or without an associated turbocondenserand turboexpander) for use in a refrigerant-based air-conditioningsystem. The system may be implemented for a variety of uses, including arefrigerator, air conditioner, heat pump, and other heating or coolingsystems using a compressible refrigerant. The turbocompressor may alsobe used for the purpose of a more-energy-efficient method forcompressing a gas prior to transportation by pipeline or by container.In such cases, the transported gas is broadly termed herein as“refrigerant”, and may be cooled without necessarily changing phase to aliquid. The device is termed a turbocompressor, because it compressesthe refrigerant (gas, etc.) via the rotation of a wheel-like spokedturbo fan that will be described in detail below. Likewise, the optionaladditional components termed a “turbocondenser” and “turboexpander” arecalled such because they accomplish condensation and expansion,respectively using a rotating apparatus.

I. Stationary Plenum Turbocompressor

FIG. 2 is a block diagram of an exemplary air-conditioning/coolingsystem loop 200 comprising a precompressor 250, an isothermalturbocompressor 300, an expansion valve 225 and an evaporator 210,connected sequentially by conduit 220. The precompressor 250 performscompression until the temperature of the refrigerant fluid rises to thatof the warm compartment, typically that of the outside atmosphere. Theisothermal compressor 300 completes the required compression whilesubjecting the refrigerant to simultaneous cooling (with possiblecondensation), keeping the temperature of the refrigerant close to thatof the outside atmosphere. From the expansion valve 225, the expandedrefrigerant then enters the compartment 210 where a flow ambient air (oranother fluid) is passed through the compartment 210 possibly using afan 240 or other source of flow. As described above, the fan 240 orpossible other source of flow directs the air/fluid over coils 231within the loop or circuit 200 to exchange heat from the air/fluid withthe refrigerant as shown. Notably, the conventional compressor/condenserarrangement such as that illustrated in FIG. 1 (110), employing twodevices in sequence to perform the two heat-transfer operationsseparately in a continual cycle (flow arrows 220) through the loop 200,has been substituted with a precompressor 250 and an isothermalturbocompressor 300 according to an illustrative embodiment. Inoperation, the (higher-heat) refrigerant, in its gaseous form, flowsthrough the precompressor 250 and, in a partially compressed state,enters isothermal turbocompressor 300 via a stationary inlet tube 310,as described in greater detail below, with reference to FIGS. 3 and 4.The isothermal turbocompressor 300, as will be described in greaterdetail below, performs additional compression via centrifugal forceexerted on a set of spokes spinning under the drive of an electrically(or other form of motive power) driven motor 350. Such compressionoccurs within the spokes 330 after refrigerant is relatively evenlydistributed thereinto via the hub 320. The motor 350 can be singlespeed, multi-speed, or variable speed as appropriate. Likewise, the sizeand power of the motor is highly variable.

Notably, the isothermal turbocompressor 300 is constructed and arrangedsuch that it also performs the cooling, which may or may not includeassociated condensation, by drawing air or other cooling fluid acrossthe device. In this manner, the fluid output 220 of the isothermalturbocompressor 300 is a cooled, elevated-pressure refrigerant, similarto the output of a conventional compressor and condenser (110 and 120 ofFIG. 1) combination, but accomplished using the precompressor 250 andisothermal turbocompressor 300, as opposed to a more-energy demandingcompressor 110 and a separate device for performing the condensation ofrefrigerant in an air-conditioning system.

The precompressor in this embodiment can comprise an axial pistonrefrigerant compressor that is driven via a belt or other powertransmission using a separate motor 252, or a drive assemblyinterconnected with the turbocompressor 300. The structure or theprecompressor is highly variable. As will be described below, theprecompressor can be integrated with the turbocompressor in variousembodiments.

More particularly, as shown in FIG. 3, which is a perspective view ofthe isothermal turbocompressor 300, the refrigerant flows undermass-flow pressure (initially generated by action of the precompressorand carried through the fluid loop) through an inlet tube 310 having astationary, non-rotating inlet cap 312. The refrigerant collects in acentral hub 320 that defines the rotating component of the isothermalturbocompressor 300. The inlet cap 312 and the central hub 320 have anappropriate seal therebetween (not shown in FIGS. 3 and 4) to preventleakage of the refrigerant to the exterior, as will be described ingreater detail below with reference to FIG. 8, which details thecentral-hub sealing components of the isothermal turbocompressor.

The isothermal turbocompressor 300 of the present embodiment furtherincludes a plurality of spokes 330 extending radially outwardly from thecentral hub 320, that terminate at a shared circumferential (circular)rim 366 that affords the rotating component (hub 320, spokes 330 and rim366 the general appearance of a spoked wheel. As shown, the illustrativewheel defines six spokes 330 that radiate outwardly from the central hub320 at equal circumferential increments. However, in alternateembodiments the number of spokes is highly variable, and can depend, inpart, upon the volume of airflow desired to achieve the cooling of therefrigerant during the air conditioning process. Likewise, a greatervolume of refrigerant can be directed through an increased number ofspokes. The movement of refrigerant through the spokes is now furtherdescribed.

In this embodiment, the spokes 330 each define a spiral shape, whentaken in plan (top or bottom) view. In alternate embodiments, they candefine a straight or segmented shape, among other possible shapes,including three-dimensional shapes. By three-dimensional, it is meantthat the spokes can deviate in part above and below a planeperpendicular to the rotational axis. As described further below, eachof the spokes 330 supports at least one conduit, i.e. a tube or hollowpassage 332 through which the refrigerant flows from the central hub 320to an exterior plenum 340, where it is collected (described below), andthen is expelled (under pressure) from the stationary plenum via anoutlet tube 342.

The above-described electric motor 350 drives a shaft 352, and can bedirectly driven, or be part of a geared transmission. The shaft 352rotates the central hub 320 (and thus also the interconnected spokes 330and their outer rim 366). In operation, the rotation of the shaft 352causes the central hub 320 and spokes 330 to spin, and the centrifugalforce exerted on the central hub 320 and the spokes 330 thereby causesthe refrigerant within the central hub to be outwardly driven throughthe tube or passage 332 in each of the spokes 330. The outward drivingforce thereby pressurizes the refrigerant (i.e. providing thecompression stage of the cycle) at the plenum 340.

The spokes 330 can be formed in accordance with a spiral curve so thatthe angle at which the spoke attaches at the circumferential rim 336 cancause the circumferential (azimuthal) component of the velocity of theexiting refrigerant to negate, totally or partially, the rotationalspeed of the rim at that point. In this arrangement, the velocity of therefrigerant at the point of its entrance into the plenum is nearlyradial and the kinetic energy associated with the unproductivecircumferential speed is reduced or eliminated.

With further reference to the passage of refrigerant from the inlet cap312, into the spokes 330, FIG. 4 is a cross-sectional view of thestationary inlet cap 312 and rotating central hub 320 of the isothermalturbocompressor 300, as taken along line 4-4 of FIG. 3. The refrigerantenters the central hub 320 via an inlet tube 310 from the system'srefrigerant loop (FIG. 2). In general, the turbocompressor drives themass flow of refrigerant through the loop so as to provide a continuousflow cycle. From the inlet tube 310, the refrigerant enters the innervolume of the central hub 320. As described below, a rotationalmechanical face seal (omitted in FIG. 4, but described in FIG. 8 below)between the hub 320 and inlet cap 312 prevents leakage of refrigerant tothe environment from the inner volume of the hub 320 as it rotates withrespect to the inlet cap 312. While a rotating mechanical face seal isemployed (see FIG. 8) in an illustrative embodiment, any appropriatesealing technique can be employed to seal the refrigerant within thecentral hub 320 (and inlet cap 312).

As further illustrated in FIG. 4, the motor drive shaft 352 rotates thecentral hub 320 at a predetermined rate, and thus spins the attached,radially outwardly directed spokes 330. The spinning of the central hub320 causes a centrifugal force to be applied to the refrigerant therein,which thereby causes the refrigerant to flow radially out of the centralhub, in a direction of the arrows 410, through the holes or ports 420 inthe hub wall. The holes or ports 420 respectively interconnect with eachspoke conduit (i.e. the tube or passage 332) so that the refrigerantflows radially outwardly through each tube or passage 332.

As described in greater detail with respect to the cross-sectional viewof FIG. 5, the spokes 330 each define a cross-sectional shape thatincludes a top fin section (or “top fin”) 510 and a bottom, oppositelydirected bottom fin section (or “bottom fin”) 512, that togethergenerate movement of the ambient air (airflow) via aerodynamic lift asthe spokes are rotated. This airflow thereby draws air across the spokesof the isothermal turbocompressor in the manner of a fan as the motor350 drives the hub 320. The airflow, having a temperature that isgenerally lower than that of the compressing refrigerant, causes therefrigerant to cool and possibly change phase to a liquid as ittransfers heat to the cooler air drawn across it (i.e. the refrigerantcan undergo a condensation cycle) in the depicted direction according tothe arrows 524.

Note, as used herein, terms such as “up”, “down”, “side”, “top”,“bottom”, “inside”, “outside”, and the like, are meant as conventionsonly and not as absolute directions/orientations. Also, the ambient airmay be replaced by another fluid, including gas or liquid, suitablychosen to perform the cooling action.

The refrigerant flows through the hollow passage 520 of the depictedtube 332 (arrow 522) based on the rotationally induced centrifugalforce. The spokes 330 are constructed and arranged such that they havean upper fin portion 510 and a lower fin portion 512 with the thickenedcentral region containing tube 332 therebetween that together form ablade-like structure that, when in rotation, acts as a fan blade. Theupper and lower fin portions 510 and 512 collectively form a slanted finblade that generates lift, thereby impelling atmospheric air or anotherambient fluid in the space between the spokes 330. The blade generallyassumes a non-parallel and non-perpendicular (slant) angle AS withrespect to the hub's rotational axis A (see also FIG. 3). This slant andcross-sectional geometry of the airfoil-like blade structure (along withthe rotational speed of the hub) controls the volume of airflow (arrows524), that is drawn past, and in contact with the spokes 330 to therebyconduct a certain amount of heat from the refrigerant passing within thetubes 332. The blade slant angle AS is highly variable, as is the crosssection geometry of the blade. Also, while a tube 332 is located at thecentral region in this embodiment, it is expressly contemplated that thetube or other conduit(s) can be located more-adjacent to an upper orlower edge of the blade/spoke. For example, the tube can be placedcloser to the leading edge of the airflow in an alternate embodiment.

The arrow 530 shows the exemplary rotation of the spokes 330 and rim 366relative to an annular well 360 of the stationary plenum 340. Thisrotation, combined with the structure of the blade shape of the spokes330, provides for the depicted airflow down and past the spokes. In thismanner, the refrigerant transfers its heat to the cooler air that isbeing drawn toward the spokes by their rotation. In other words, theslanted, airfoil-shaped spokes 330 act as fan blades that can be rotatedto provide a continuous flow of cooler air in contact with the surfacethereof.

In alternate embodiments, it can be desirable to provide each spoke ofthe isothermal turbocompressor 300 with a plurality of oblong passagesor tubes formed within its cross sectional structure. Providing aplurality of tubes or passages provides more contact area for therefrigerant with respect to the spoke's surface, and thereby increasesthe amount of heat transfer during compression. FIG. 6 shows across-sectional view of a multi-tube spoke 600 according to an alternateembodiment. As shown, the spoke defines an upper fin portion 610 and alower fin portion 612, which each taper in opposing directions togenerate lift during rotation. This lift draws air across the blades asdescribed above to thereby cool the refrigerant. The fin portions 610,612 can define any shape, but illustratively extend in opposingdirections as identical, mirror-imaged airfoils as shown. An asymmetricairfoil that optimizes air movement in a given direction can be providedin alternate embodiments hereto. The cross-sectional shape of thespoke/blade 330, 500 in the embodiments herein can be angled in anopposing direction so as to direct airflow in an opposing direction fora given rotational direction.

Notably, the illustrative spoke 600 includes a plurality of tubes orpassages 621, 622 and 623 within its cross section through whichrefrigerant flows to undergo the compression cycle of an airconditioning or refrigeration process. As described, a plurality oftubes potentially increases the cross sectional area of the overallrefrigerant conduit in each spoke without overly increasing thethickness of the spoke's blade geometry (and thereby reducing its liftproperties or increasing its aerodynamic drag). This allows for greaterrefrigerant surface area in contact with the heat-conducting surface ofthe spoke and a higher refrigerant mass flow rate, or alternatively aslower flow of refrigerant at equal overall mass flow rate, therebyincreasing the isothermal turbocompressor's cooling capacity and itsdegree of heat transfer. In general, this multi-tube arrangement canpermit the given flow volume of refrigerant to transfer increased heatwhen compared to a single passage/tube embodiment to thereby furtherimprove compressor efficiency. Additionally, if several passages areprovided through each spoke, then these tubes can define varieddiameters or varied cross-sectional shapes within the same spoke (forexample, a larger circular tube in the center flanked by a pair ofsmaller elliptical passages—one smaller passage located adjacent to eachfin edge). A multi-tube blade can also be customized for particularapplications by varying the number of tubes provided within each spoke.That is, in some embodiment, two tubes can be employed, in otherembodiments, 4 or 5 tubes can be employed (for example). The crosssection shape and overall area of an individual tube or passage can alsovary along its length along the spoke, being, for example, wider nearthe entrance and progressively narrower down the length of the spoke toconcentrate the fluid as it becomes pressurized.

It should be clear that a wide range of possible passage shapes andarrangements can be defined within the walls of the spoke. Likewise avariety of flat shapes, symmetrical airfoils and asymmetrical airfoilswith tan appropriate slant angle (or range of slant angles) can beemployed. In general, internal passage shapes that allow greater contactbetween the fluid and the surface area of the passage, and/or those thatprovide a thinner wall between the cooling fluid and the fluid are oftendesirable to increase heat transfer. In further embodiments, the spokescan define a variable geometry in the manner of a variable-pitchaircraft propeller to increase or decrease airflow (and heat transfer)for a given motor rotation rate. Electromechanical actuators, steppers,servos or solenoids operatively connected to the hub and/or the rim caneffect the change in pitch/slant angle. Other devices, such as intake oroutflow louvers, placed in line with the turbocompressor's air/fluidflow can also be used to vary the flow across the spokes.

Referring again to FIG. 3, the outer rim 366 that surrounds the spokes330 rides within a circumferentially annular well or groove 360 of acircular, stationary plenum 340 of the isothermal turbocompressor 300.The pressurized refrigerant exits the spokes 330 via through-holes orports in the rim 366, shown in greater detail in the cross section ofFIG. 7. The refrigerant flows from the through-holes 730 to be collectedin the stationary plenum 340 at an annular conduit 720 that forms aradial-outward coaxial extension of the annular well 360. Thethrough-holes or ports 730 are typically provided in numbers and shapesthat accommodate the number and shapes of passages at their terminalpoint of the spokes (according to the various geometries contemplatedherein), in order to provide smooth passage of the refrigerant into theplenum 340. The cross-sectional shape of the annular conduit 720 thatreceives refrigerant from the through-holes 730 is also highly variable,and by way of example, is depicted as a rectangular cross section.

The illustrative annular well 360 of the stationary plenum 340 defines aheight HW that is sufficient to allow the height HR of the rim 366 torotate within the stationary plenum 340. Appropriate mechanical faceseals are used to prevent refrigerant loss as the rim 366 rotates withrespect to the plenum 340, as will be described in greater detail belowwith reference to FIG. 9. The high-pressure, cooled refrigerant exitsthe stationary plenum 340 via at least one outlet tube (theabove-described outlet 342 shown in phantom in FIG. 7) located along theplenum's outer wall 370, or another plenum wall (e.g. the top and/orbottom plenum walls), and in fluid communication with the conduit 720.The pressurized, cooled refrigerant can thereafter be drawn through anexpansion valve (225) that reduces its pressure and temperature, suchthat the refrigerant may absorb the warm air within a compartment asperformed in conventional air-conditioning and other cooling systems.Note, in an alternate embodiment, the pressure-reducing expansion valvemay be incorporated in the isothermal turbocompressor (for example, as acomponent placed along outlet tube 342 or components affixed to each ofthe several through-holes 730 along the rim 366).

As described below in greater detail, with reference to FIG. 9, the rim366 is sealed within the stationary plenum 340 using an accompanyingrotating mechanical face seal therebetween so as to retain thepressurized refrigerant within the well 360 and circumferential conduit720 of the stationary plenum 340.

Note that the spokes 330, hub 320 and rim 366 can be constructed from amaterial as a unitary fan/wheel structure (for example, an aluminumcasting), or from a plurality of materials that are assembled togetherto form the fan structure. In general, the fins are desirablyconstructed from a material with relatively high thermal conductivity,such as metal. Other components, such as the rim 366, can be constructedfrom other materials where appropriate, such as a composite. However,the material choice for the fan and other elements of theturbocompressor is highly variable. Such materials are generallyselected for cost, ease of working, ability to withstand pressure andmechanical stress (for example, the stresses imparted by centrifugalforce), durability, and thermal properties.

FIGS. 8 and 9 detail rotational seals provided, respectively at each ofthe hub 320 and the plenum 340 according to an illustrative embodimentof the isothermal turbocompressor 300. As shown, the illustrative sealsare known generally to those skilled in the art as mechanical faceseals. Mechanical face seals generally comprise seals that employ aspring-loaded/fluid-pressure-biased primary ring, as will be described,and a mating ring, to provide a slidable sealing surface therebetweenwhich serves to maintain pressurized liquids and/or gases from leakingaway from the volume in which they must remain confined. In general, theaxially-movable primary ring is secured to one rotating member while themating ring is axially fixed, and secured to the opposing rotatingsurface. The primary and mating rings confront each other along acircumferential sealing face that defines a relatively low-friction,sliding interface therebetween. One ring may be constructed of a softermaterial than the other to prevent abrasion that can eventually causefluid leakage through the interface. The primary ring is typicallybiased toward the interface by a spring to maintain the seal while thecomponents are stationary (non-rotating), and is arranged so thatincreased fluid pressure forces the primary ring to bear more forciblyagainst the mating ring to enhance the seal at higher pressures. By wayof further background mechanical face seals, for use according toillustrative embodiments herein are shown and described in, PRINCIPLESAND DESIGN OF MECHANICAL FACE SEALS, by Alan O. Lebeck (1991). Thisreference should provide a general guide to the reader on theconstruction of a variety of commonly employed mechanical face seals foruse in rotating assemblies, which require fluid to be maintained withinthe enclosed space between the rotating components.

FIG. 8 is a more-detailed illustration of the cross-sectional view ofFIG. 4, showing exemplary sealing components located between therotating central hub 320 and the stationary inlet cap 312. The primaryring 820 is fixed about the central hub 320 and provides compensationand flexibility to allow for small relative axial and angular motion ofthe relative parts. The primary ring 820 comprises a base ring 822 thatis fixed about the central hub 320 (as shown by the fasteners or pins823 denoting attachment to the adjacent structure) and a primary sealring 824. The fixed components can be attached by any acceptableattachment mechanism. The primary ring 820 is generally sealed frominfiltration via a flexible annular cover 825 that extends between thebase ring 822 and the seal ring 824 so as to cover a series of biasingsprings 828 therebetween equally spaced around the circumference of thecentral hub 320. The primary ring 820 is biased by the springs 828 in adownward direction (arrow 827) to create the sealing surface 810 betweenthe primary ring 820 and the mating ring 830. The mating ring 830 is,thus, fixedly attached (by exemplary pins 823) to the inner surface ofthe stationary inlet cap 312. As shown, a planar, annular sealingsurface 810 is thereby provided between the biased primary ring 820 anda mating ring 830. The springs 828 bias the seal ring 824 of the primaryring 820 into contact with the mating ring 830 to seal the refrigerantwithin the isothermal turbocompressor and to prevent potential leakagewhile the components are stationary. As loop pressure is generatedduring compressor operation, the arrangement of the seal ring 824 withrespect to the volume space 840 causes the pressure to bias downwardly(arrow 827) on the seal ring 824, so as to increase its engagementpressure against the mating ring 830. Note that a secondary seal (O-ring850) can be provided against the outer wall of the hub 320. This seal850, along with the flexible connection between the base ring 822 andsealing ring 824, allows for small axial and radial movement of the huband inlet cap with respect to each other.

The mechanical face seal arrangement, as shown in FIG. 8, allows therotating central hub, as fixed on the shaft 352, to rotate within theinlet cap 312, while sealing the refrigerant therein. A similarmechanical face seal arrangement is provided to seal refrigerantcollected within the stationary plenum 340, as the rim 366 rotatestherein, which is now described in further detail.

FIG. 9 is a more-detailed illustration of the cross-sectional view ofFIG. 7, showing exemplary sealing components that provide a sealingsurface 910 between the rim 366 and the circumferential annular well 360of the stationary plenum 340. In an illustrative embodiment, theexemplary sealing mechanism employed between the rim 366 and the well360 is also a rotating mechanical face seals, similar to that describedwith reference to FIG. 8 above. However, any acceptable seal that allowsfor the containment of fluid under pressure while a pair of componentsrotate with respect to each other can be employed in alternateembodiments

As shown, a pair of opposing mechanical face seals is employed betweenthe rim 366 and the well 360. Each of these seals includes a primaryring 920, comprising a fixed base ring 922, which is attached to thestationary plenum 340 (pins 923). The primary ring 920 further comprisesan axially movable seal ring 924 which contacts the mating ring 930,fixed to the ring 366, to seal the refrigerant within the stationaryplenum. The primary ring 920 is sealed with a cover 925 to resistinfiltration of the refrigerant therein, and further comprises a spring928 (or multiplicity of discrete springs positioned about thecircumference), which biases the primary seal in a direction against themating seal 930.

The mating ring is attached to the ring 366 (pins 923), and provides forthe slidable seal interface 910 so as to prevent unwanted leakage of therefrigerant from the stationary plenum. This seal is highly desirable toretain the refrigerant in the stationary plenum so that it may bedirected out of the stationary plenum via outlet tube 342, such that itmay be employed by an air-conditioning or other cooling, heat-pumping,or heat-exchange arrangement.

Note that the mechanical face seals depicted are only meant to show anexample of a possible seal arrangement for use with the components ofthis embodiment, and any acceptable technique known to those of skill inthe art for appropriately sealing the refrigerant within the compressorat its points of motion is expressly contemplated. Seal arrangementother than, or in addition to, the depicted mechanical face seals areexpressly contemplated. Likewise, while not shown, the hub 320 and therim 366 can each be supported by appropriate bearing structures thatensure an aligned and low-friction rotation between these elements andthe respective stationary components (inlet cap 312 and plenum 340). Ingeneral a variety of bearing structures and/or sealing mechanisms can beprovided between the inlet cap 312 and plenum 340. Implementations ofsuch bearing structures and/or sealing mechanisms should be clear tothose of ordinary skill in the art.

With reference now to FIG. 10, the illustrative turbocompressor 300 isshown installed in a non-cyclical fluid circuit 1000. In this example,the (simplified) circuit 1000 is a natural gas pipeline that originatesat a gas source (either a well or terminal) 1010 and extends to theillustrative turbocompressor 300 (sized and arranged appropriately to agas pipeline application) via a pipe or conduit 1020 through which thegas flows (arrow 1030). The turbocompressor 300 is operated to increasethe incoming gas' pressure, while simultaneously cooling it in anisothermal, or near-isothermal process so that it can bemore-efficiently transferred (arrow 1040) from the compressor outlet 342to a pipeline 1050. The exemplary pipeline 1050 directs the cooled (buttypically non-liquefied) and pressurized gas to a storage tank 1060 orother destination. It is contemplated that a variety of intermediatevalves, conduits, devices, and the like can be interposed between thesource (1010) and destination (1060), including additionalturbocompressor stages. This example is one of a variety ofnon-refrigeration-based applications in which the illustrativeturbocompressor of this invention can be employed. Thus, as used hereinand as described above, the term “refrigerant” is taken broadly toinclude a cooled gas transported through the turbocompressor in apoint-to-point circuit.

More generally, while the turbocompressor of this invention iswell-suited to applications such as domestic or automotiveair-conditioning, heat-pumping, refrigeration and/or cooling, the use ofthe illustrative isothermal turbocompressor in a variety of types andscales of applications is expressly contemplated. In a typicalapplication, however, the diameter of the spoke/fan portion is in anapproximate range of 20 inches to 6 feet, while the external area ofeach spoke is approximately 0.1 to 4 square feet, and the number ofspokes is approximately in the range of 6 to 24. Operating in arotational speed range of approximately 400 to 2000 RPM, using a motorof approximately 0.5 to 2 HP, the unit should be able to accomplish heattransfer in a range of approximately 100 to 400 BTUs per minute. Ofcourse, these parameters are only exemplary of a wide range of sizeand/or performance specifications for the turbocompressor of thisinvention.

While the use of the illustrative turbocompressor in a coolingapplication is shown and described above, it is expressly contemplatedthat the efficient isothermal properties of the compressor can beemployed in a heating application—for example, in a heat pumpembodiment. Accordingly, the “heat” shown exhausted from theturbocompressor 300 in FIG. 2 can be ducted or otherwise collected in aheating arrangement, and used to heat a desired object or space inaccordance with conventional techniques.

II. Turbo-Compressor-Condenser-Expander with Open Frame Dual-Spoke FrameStructure

The open framework structure shown in FIGS. 11-14 avoids designchallenges resulting from implementing a stationary plenum andassociated mechanical face seal arrangement requiring a large-diameterexternal seal. It also permits additional heat transfer (with possiblecondensation) and expansive decompression. An illustrative embodiment isshown which provides an isothermal turbo-compressor-condenser-expander(ITCCE) 1100 of FIG. 11. As shown, a precompression hub 1110 (thestructure and operation of which is described further below) is at thecenter of the ITCCE 1100, in to which refrigerant flows to undergo apreliminary compression during the refrigerant cycle. The precompressedrefrigerant then enters the ITCCE 1100 through a stationary inlet tube1115 and down through a central passage in the axle 1117 to the first,inlet central hub 1110. As shown in greater detail in FIG. 14,precompression can be alternately implemented using, for example, aseparate, discrete axial piston refrigerant compressor connected byconduits within the refrigerant loop. By way of example, this separateprecompressor can be a type used in a conventional airconditioning/refrigeration system application. As described furtherbelow, the precompressor increases the refrigerant temperature, andallows it to flow into the turbocompressor stage at an appropriatetemperature and pressure.

Referring back to FIG. 11, a plurality of spokes 1120 extend radiallyoutwardly from the central hub 1110 in the form of a wheel-like spokeframe structure. As shown by arrow 1121, during rotation of the spokes,refrigerant is impelled through radial fins or blades 1130 to a maximumpoint of pressure and temperature at the ITCCE perimeter 1125. In anillustrative embodiment, by way of example, the overall framework has adiameter of approximately 3-4 feet at its perimeter and a height(axially) of approximately 6-16 inches. However, the size of theframework is highly variable and the dimensions provided above for thestationary plenum embodiment can also be applied to this embodiment. Thefins or blades generate an airflow over their surface to promote airexchange as they rotate during operation. As used herein, the term“spoke” can refer interchangeably to a complete structure defining anintegral blade and internal passage, pipe or conduit, or can define anunderlying framework structural member to which a conduit and/or bladeare attached. As shown, the blades are mounted on, or surround, thespokes of the framework and associated conduits. The blades are inthermal contact with the conduits in each embodiment. The radial blades1130 promote the air exchange as shown by the arrow 1135 indicating theforce of drawing ambient outdoor air down through the ITCCE 1100. Therefrigerant then flows down through axial blades 1140 as shown by arrow1122. The blades 1140 further promote significant air exchange (andresulting isothermalism of the possible condensation of the refrigerant)by improving the amount of heated air that is expelled, as shown byarrow 1145. In an alternate embodiment, the orientation of the blades1130 and 1140 may be modified or the direction of rotation of the devicereversed to force the air to follow a path opposite to that described byarrows 1135 and 1145.

The elbows connecting the terminal ends of the axial blades 1130 to theentrance ends of the axial fins 1140 may possibly be interconnected by asolid rim to increase the physical rigidity to the device.

These fins are typically two to eight inches wide, and their width maybe uniform from one side to another. A variable width of the fins ispossible and expressly contemplated. It is desirable that the materialsused for fins 1140 possess high thermal conductivity but may otherwisebe highly variable. The fins can be single faced with a single piece ofsheet metal or other material. They can be encased in a thermallyconductive material, as shown in the illustrative embodiments.

The blades or fins according to illustrative embodiments can be sizedand arranged to be no more than approximately half the diameter of thedevice, as well as constrained as to not be so large that the resultantstructure is insufficiently open, so as to admit and expel the desiredquantity of air for heat exchange. In an example, a ratio a maximumsolid surface (blade surface, adjacent framework, etc.) to open voidscan be approximately of 70%. The dimensions should generally allowsufficient extended surface to reject the heat from the refrigerationprocess. In an illustrative embodiment, there are provided twelve radialtrapezoidal (basically triangular) perimeter-shaped blades measuringapproximately 1 inch wide adjacent to the first central hub andapproximately 6 inches wide at the outer perimeter, and having a radiallength of approximately 15 inches. The axial blades are generallyrectangular in perimeter shape, measuring approximately 8.5 inches (inthe axial direction and 4 inches wide. As depicted, the radial and axialblades can be canted at an angle with respect to a tangent line of theframework's circular outer perimeter (for example 3-7 degrees) toenhance air movement through the framework, in the manner of an impellerfan. As to materials of construction, one would not want to be undulylimited, but thermal conductivity is an essential aspect to promote heattransfer between refrigerant flowing inside the blades and air impelledon the periphery of the blades.

The geometry and structure of the blades are highly variable to attainthe desired heat transfer characteristics depending on the surroundingsystem, leading to the condensation if so desired. The blades can behollow such that refrigerant fills the entire blade to undergocompression. The blades can be formed of a molded structure that issolid or semisolid having one or more conduit therethrough, for exampleas shown in FIG. 6 showing multiple conduits through a solidblade-shaped spoke. In each embodiment, the blade is in thermalcommunication with the conduit.

The surface of the blades is also highly variable, and can range from aflat smooth surface, to a textured surface for increased surface areaand structural integrity. The surface can be textured or rippledaccording to the illustrative embodiments.

After passing through the blades 1140, the refrigerant then travelsthrough conduits in supported by the second set (the lower set asdepicted) of spokes of the ITCCE 1100 (shown as spokes 1220 in bottomview of FIG. 12). The refrigerant then exits through a stationary outlettube 1150. The motor drive 1160 rotates the central axle 1117 of theITCCE 1100 at a desired rate, ranging between several hundred to twothousand revolutions per minute (RPMs), to rotate the spokes of thedevice such that the refrigerant undergoes centrifugal force fordecompression during refrigeration or another heat exchange cycle. Inthis embodiment, the motor 1160 is shown, by way of example, located inan inline configuration driving the axle 1117. In alternate embodiments,such as described further below, the motor can be interconnected via agear train, belt-and-sheave assembly, or other appropriate powertransmission mechanism. The motor can be driven at a constant or avariable speed of rotation.

As shown in FIG. 12, the refrigerant flows through the conduits of thelower spokes 1220 to undergo decompression into a lower pressure, lowertemperature fluid, as it flows into an outlet, central hub 1240. Therefrigerant then flows coaxially with the central axle 1117 and into astationary outlet collection space 1235.

The lower spokes 1220 may be straight or curved. It is desirable thatthe spokes 1220 be made of a thermally resistant material in order tominimize heat transfer with the surrounding air. Alternatively, they maybe enveloped in a thermally insulating material, either singly ortogether. The spokes may otherwise be made from a variety of materials.The set of spokes 1220 and their insulation may be embedded inside asolid matrix (not shown in the illustration) so that the exteriorsurface of the lower wheel be smooth and offer low aerodynamicresistance while in rotation. Alternatively, the embedding matrix mayserve as the thermally insulating material.

The ITCCE 1100 includes a covering disc 1250 on its bottom side, underwhich the lower spokes 1220 pass, to maintain stability of the ITCCE1100 and improve structural strength (as well as to isolate the adjacentradial conduits from airflow generated by the axial and radial blades1220, 1130). However, in further illustrative embodiments, the disc canbe removed leaving only a spoke arrangement. The conduits of the second,lower spoke arrangement performs the expansion of the refrigerant as itflows back to the central axis of the ITCCE 1100. This decompressiongenerates a physical torque that is similarly directed to the rotarymovement of the device, thereby providing mechanical energy thatcontributes to the spin of the jointly rotating members of the ITCCE1100 and decreasing the mechanical energy exerted by the motor drive1160

Reference is now made to FIG. 13 showing a cross-sectional schematicview of the flow of refrigerant within the ITCCE 1100. The refrigerantenters through an inlet tube 1115 as shown by arrow 1304. The stationaryinlet tube 1115 feeds into an inlet collection tank 1119 that isrotationally fixed and joined by a rotary seal assembly 1305 to acoaxially rotating axle 1117, which provides an internal passage 1307for refrigerant to pass through the axle 1117 into the hub 1110. Thediameter ‘D’ of the internal passage can be and eighth of an inch tothree-quarters of an inch in various illustrative embodiments. Othersizes, both smaller and larger, are contemplated for the passage and thespokes of the ITCCE 1100. This embodiment employs a single central axle1117 that extends from the motor 1160 through the outlet rotary sealassembly 1330, through the lower hub 1240 and upper hub 1110 andterminates at the inlet rotary seal assembly 1305. The axle is hollowalong at least two segments to provide for the inlet and outlet ofrefrigerant into the conduits 1120 of the ITCCE 1100. The bearing sealassemblies 1305 and 1330 can be of any acceptable construction describedabove with respect to the illustrative embodiment of FIG. 8 to allow therefrigerant to pass therethrough while the axle 1117 rotates. In oneexample the rotary seals can consist in device 008-12230-32, ahigh-speed air-hydraulic union (see by way of example:http:www.rotarysystems.com/series-008). Another exemplary rotary fluidunion is available from Deublin of Waukegan, Ill., as model number1102-070-029. This union comprises a ⅝″-18 UNF RH 21 1102-070-079 UNF LHcombination. This device uses a spring loaded carbon graphite stationaryface combined with a ball bearing supported polished steel rotatingface, with a metal crush washer face seal. The size and scale of theunions used in this embodiment are proportional to output and scale ofthe ITCCE. Also, while not shown, at one or more points along the axle,there may be provided bearings for mounting the rotating assembly of theITCCE within a stationary framework.

The refrigerant flows as shown by arrow 1306 down into the central hub1110. The refrigerant then flows outwardly in the first, upper set ofradial conduits of the spokes 1120 as shown by arrows 1310 out from thecentral hub 1110. The axle 1117 is hollow over a length that extendsfrom its end inside the rotary seal 1305 to a place where its diameterincreases at the hub 1110. The axle at its larger diameter of the hub1110 is perforated with a plurality of radial passages 1315 thatpenetrate into the axle shaft 1117 so as to create conduits to andthrough the spokes 1120 of the ITCCE 1100 for the flow of refrigerant.The spokes are fastened to the shaft 1117 at these conduits by screws,fasteners, or other appropriate securing mechanisms 1317. Therefrigerant flows radially out from the central hub 1110 in the firstset of radial conduits of the spokes 1120. These conduits are surroundedby radial blades 1130 in thermal contact therewith. The refrigerantthereby achieves a maximum temperature and pressure at the ITCCEperimeter 1125.

The refrigerant then flows down through the axial blades 1140 as shownby arrows 1312 and heated air is passed out from the axial blades 1140see arrow 1145 of FIG. 12). The refrigerant loses heat, possibly causingcondensation. The refrigerant then flows, as shown by arrows 1314, backto the second, outlet central hub 1240 of the central axle 1117, and inthe process undergoes expansion and its temperature drops. The thermallyinsulated tubes end at holes on the periphery of the shaft to which theyare fastened by screws or by other securing mechanisms 1317. Therefrigerant then flows down the central axis as shown by arrows 1320.The rotating seal assembly 1330 is rotatably fixed and joined to thestationary collection tank 1235. The axle 1117 rotates (arrow 1350)within the stationary collection tank 1235 via the rotating sealassembly 1330. The refrigerant flows out of the stationary collectiontank 1235 via outlet tube 1150 as shown by arrow 1360.

In an operative embodiment, it is typically desirable to perform aseparate, discrete precompression of the refrigerant prior to admittingit into the ITCCE at inlet tube 1115 in order that its temperatureexceed the temperature of the surrounding air at perimeter point 1125.FIG. 14 shows a compression arrangement that includes both a discreteprecompressor and an ITC according to an illustrative embodiment. Theair-conditioning/heat-exchange system 1400 employs an ITCCE 1100.

FIG. 14 is a block diagram of an exemplary air-conditioning/coolingsystem loop 1400 comprising an ITCCE 1100 that performs the compression,cooling (with possible condensation) and expansion of refrigerantrequired to cool the airflow through compartment 1410. Refrigerantexpansion/decompression occurs within the second radial set of conduits1220. The expanded refrigerant enters directly from the outlet member1150 to the compartment 1410 free of any separate expansion valve. Inalternate embodiments, an optional expansion valve may be used ifdecompression along the return radial conduits is incomplete. A flowambient air (or another fluid) is passed through the compartment 1410possibly using a fan 1440 or equivalent impeller/mass-flow driver. Asdescribed above, the fan 1440 directs the air/fluid over coils 1431within the loop or circuit 1400 to exchange heat from the air/fluid withthe refrigerant as shown. Notably, the conventional compressor/condenserarrangement such as that illustrated in FIG. 1 (110), employing twodevices in sequence to perform the two heat-transfer operationsseparately in a continual cycle (flow arrows 1420) through the loop1400, has been substituted with a single ITCCE 1100 and a pre-compressor1450 according to an illustrative embodiment.

In operation, the (higher-heat) refrigerant, in its gaseous form, entersthe pre-compressor 1450 to undergo pre-compression. As shown, thepre-compressor is driven by a motor 1460 via a belt 1465, however thecompressor can be driven according to any system or method forinitiating the compression. The pre-compressed refrigerant then entersthe ITCCE 1100 via a stationary inlet tube 1115, as described in greaterdetail above with reference to FIGS. 11-13. The ITCCE 1100, performs thecompression via centrifugal force exerted on a set of spokes spinningunder the drive of an electrically (or other form of motive power)driven motor 1160. Such compression occurs within the spokes afterrefrigerant is relatively evenly distributed thereinto via the hub 1110.The motor 1160 can be single speed, multi-speed, or variable speed asappropriate. Likewise, the size and power of the motor is highlyvariable. In an embodiment the pre-compressor raises the pressure of therefrigerant to approximately 5 atmospheres

Notably, the ITCCE is constructed and arranged such that it alsoperforms additional isothermal compression and performs the cooling,which may or may not include associated condensation, by drawing air orother cooling fluid across the device. The ITCCE further expands therefrigerant. In this manner, the fluid output 1420 of the ITCCE is acooled, low-pressure refrigerant vapor possibly saturated withaccompanying refrigerant liquid, similar to the output of a conventionalexpansion valve (125 of FIG. 1), but accomplished using the ITCCE 1100,as opposed to three discrete, interconnected devices for performing thecompression, condensation and evaporation cycles of refrigerant in anair-conditioning system.

FIG. 15 is a generalized graph 1500 showing the energy saved byemploying pre-compression according to the illustrative system of FIG.14, as compared with a conventional refrigeration cycle. The graph isapplicable to a variety of refrigerants, such as R-22, or more typicallyR-134a. The conventional refrigeration thermodynamic path (arrows 1530,1542 and 1554) is a 1 ton air-conditioning unit. Line 1510 shows thestate of the refrigerant as liquid, gas, or a liquid/gas mixture. Oneadvantage of the ITCCE is that it can operate in the presence of liquid,a mixture of condensing vapor and liquid, or vapor alike, as itcomprises the tubular channels with no reciprocating devices, one-wayvalves, or other similar mechanisms found in adiabatic compressors.According to a conventional compression refrigeration cycle, acompression of a supersaturated vapor is conducted because the presenceof any liquid interferes with the mechanisms of a typical compressordevice, and operation with a supersaturated vapor can preventcondensation. Because the ITCCE performs compression 1544, condensation1545 and isoentropic expansion 1550 gradually, and the gentle gradientin pressure from the axis to the perimeter follows more closely to thedefinition of a thermodynamically reversible process. Note that thefirst set of radial conduits (upper set as depicted) and associatedblades perform compression as shown by the graph segment identified byarrow 1544. The axial conduits on the outer perimeter, and associatedblades, perform condensation as referenced by the graph segmentidentified by arrow 1545.

Note that, while the term “condensation” and “compression” are usedherein, it is contemplated that some refrigerants may becomesupercritical, rather than condensing in the typical sense, wherein thedifference between vapor and liquid states in indistinct. Therefrigeration cycle still occurs when using such refrigerants, but thetemperature profile differs from that described in the graph of FIG. 15.Hence, in cases where such refrigerants that may move into asupercritical state for some or all of the refrigeration cycle (forexample CO₂ and ethane), the terms “compression” and “condensation”should be taken broadly herein to include the behavior of suchrefrigerants. Note that a supercritical condition may occur within theaxial conduits, and the condensation would occur in the second radialset of return conduits in the form of phase separation.

Arrow 1520 of the graph 1500 shows the pre-compression performedaccording to an illustrative embodiment. The arrow 1530 shows thefurther compression required of a conventional refrigeration cycle. Thusthe shaded area 1540 represents the energy saved by the system employinga pre-compressor 1450 and ITCCE 1100, as shown in the illustrativeembodiment of FIG. 14. The graph of FIG. 15 further shows the additionalenergy required to convert the gas back to a liquid of arrow 1542, notrequired for ITCCE 1100 because it can be a gas or a liquid. The ITCCEundergoes reversible (constant entropy) centrifugal decompression asshown by arrow 1550. The mechanical energy produced by thisdecompression (expansion) is communicated to the rotary device, thusreducing the energy demanded for the compression performed by the ITCCE.Furthermore, at its exit from the ITCCE, the refrigerant is in a stateof lower entropy compared to its state at the exit of the expansionvalve in a conventional system. The ITCCE thus extends the cooling time(thereby improving the amount of cooled air that is transferred) asshown by the extended cooling arrow 1555 of FIG. 15.

FIG. 16 depicts an illustrative axial cross-sectional shape for aheat-exchanging blade 1610 according to an embodiment. As noted above,the shape and structure of the fins, blades or other aerodynamicheat-exchanging elements are highly variable. In the above-describedembodiment, a diamond airfoil constructed from sheet steel or aluminumalloy is employed for ease of construction. However, other shapes areexpressly contemplated, such as that depicted in FIG. 16. This blade1610 generally defines a NACA airfoil having a symmetrical teardropshape. In this embodiment, a pair of airfoil halves 1620, 1630 isformed, in whole or in part, from cast or stamped metal, carboncomposite, or another heat-conducting material. The halves are joinedtogether using plurality of fasteners (screws, rivets, etc.) 1640, atappropriate locations along the blade surface. The blade defines,adjacent its leading edge 1650 a passage 1660 that can be filled withfluid, or house one or more fluid conduits (a single conduit 1670 inthis example). The conduit is in contact with the blade material tofacilitate heat-transfer. Additional structures can be used to increasesurface contact between the conduit 1670 and blade material. Likewise, athermally conductive packing 1680 can surround the conduit within thepassage 1660. In alternate embodiments, the blade 1610 can also beimplemented as an asymmetrical airfoil. Note that the term “airfoil” asused herein should be taken broadly to include any shape that causes aredirection of airflow thereover, including, but not limited to singlesheet blades and vanes and diamond-cross section blades. Note that,where blades are not used in the framework for heat transfer, they canbe constructed from a low-heat conducting material, such as laminatedwood or fiberglass composite. The conduit 1670 inside blade 1610 mayfollow a straight path, a sinuous path, or any other path in order topromote heat transfer between the refrigerant it contains and theembedding material.

Reference is now made to FIG. 17, which details an alternate embodimentof the isothermal turbocompressor-condenser-expander 1700. As shown, themain drive motor 1710 is mounted in an offset arrangement, andoperatively connected to the main shaft assembly 1714 by a belt andpulley assembly. A gear train or other power transmission arrangementcan be employed in alternate embodiments. The main shaft assembly 1714is generally hollow along its length between a coaxial fluid union 1720and a coaxial precompressor 1730, each described in further detailbelow. The main shaft assembly 1714 extends past the motor drive sheave1740 to fluid-transferring the central hub 1742. Axially for the hub,the main shaft assembly 1714 defines a hollow connecting shaft 1750 thatextends to the coaxial precompressor assembly 1730 of this embodiment.As described below, the precompressor assembly is driven by a secondaryshaft 1762, which is independent of rotation of the main shaft assembly1714. In an embodiment, the shaft 1762 is stationary (i.e. non-rotatingand fixed to the associated mounting assembly). In alternateembodiments, the shaft 1762 can be supplementally, or alternatively,driven by an optional drive motor 1760. The optional drive motor cancomprise a “canned” rotor that is enclosed within the housing (1910)fluid circuit and separated hermetically from the stator by a membrane.Likewise, the motor and shaft (1762) can be linked to the housing by amagnetic coupling that avoids the need for the seal 1962. The stationaryembodiment of the shaft 1962 can likewise be interconnected with thepiston assembly via a magnetic coupling that eliminates thethrough-shaft and seal arrangement depicted in FIG. 19.

With further reference to the side cross section of FIG. 18, the coaxialfluid union 1720 and adjacent main shaft assembly 1714 is shown infurther detail. This coupling provides both an outlet 1770 for cold,low-pressure refrigerant to be delivered to the evaporator assembly (inthe refrigerant loop), and an inlet 1772 for evaporated, low pressurerefrigerant delivered from the evaporator assembly back to the ITCCE.Both the inlet 1772 and outlet 1770 are provided on stationary(non-rotating) bases of rotatable fluid couplings 1812 and 1810. Theinlet coupling 1812 includes a face seal 1822 that is biased by a spring1824 into engagement with a rotating base 1826. The rotating base 1826is rotatably interconnected to the inlet base 1812 by a set of bearings1828 that allow free rotation therebetween while the face seal 1822avoids loss of fluid through the rotating joint. The rotating jointforms a hollow passage for refrigerant from the stationary inlet base1812 into the rotating shaft member 1830. The rotating shaft member 1830extends axially to the stationary outlet base 1810 that is in fluidcommunication with an external channel system 1840 formed coaxially witha central channel 1842. The channel system includes a series of passagesdisposed about the circumference of the shaft and each interconnectedwith a port 1844 in the return (lower or “second”) central hub 1742. Theoutlet base 1810 is sealed with respect to the shaft 1830 by stationaryface seals 1850.

Rotation between the base 1810 and shaft 1830 is facilitated by bearings1852. Thus, expanded refrigerant returns (arrows 1860) from the radialconduits 1752 to the hub 1742, and then travels (arrows 1862) along thepassages 1840 into the stationary outlet base, where it is directed(arrow 1864) to the evaporator via the loop.

The evaporated refrigerant enters from the loop (arrow 1866) via theinlet base 1812 and passes (arrows 1868) into the central channel 1842.The refrigerant thereafter travels axially past the hub 1714 and into(arrow 1870) the hollow connecting shaft 1750 that interconnects the twospoke hubs. The refrigerant then travels axially into the precompressor(upper or “first”) hub assembly 1730 according to this embodiment. Theprecompressor hub, like the return hub 1742 acts as an interconnectionfor each conduit and blade loop (for example, radial conduit 1780 andradial blade 1782; axial conduit 1784 and axial blade 1786; and radialconduit 1752). These hubs 1742, 1730 also support the frameworkstructure for each spoke under the rotational torque of the main drivemotor 1710.

The precompressor 1730 can be constructed in a variety of manners. Inthis example, and referring also to FIG. 19, the precompressor includesan outer housing 1910 that supports the spoke framework (not shown), anddefines ports 1920 associated with each radial compression conduit andblade assembly (1780, 1782). The housing 1910 rotates on the end of thehollow connecting shaft 1752, that is driven by the motor 1710 andassociated linkages and couplings. Refrigerant travels from theconnecting shaft 1750 into the interior of the housing 1910. The fluidthen selectively travels (arrows 1928) trough an array of suction anddischarge reed valves into cylinders 1932 positioned around thecircumference of the housing. The number of cylinders 1932 can equal thenumber of ports 1920 or a cylinder can interconnect via appropriatefluid channels in the housing 1910 with multiple ports. The cylinders1932 each house a respective piston 1934 that reciprocate within therespective cylinders based upon the interaction of a stationary (orseparately driven) swash plate 1940 and a cylinder groove 1942. Theswash plate 1940 is fixed to the shaft 1762 at a relative angle AS, asshown. The shaft moves differentially with respect to the housing1910—either due to a separate drive connection (e.g. motor 1760), or dueto the rotational differential between a fixed shaft 1762 and therotating housing 1910. The swash plate 1940 thereby rotates with respectto the pistons and its relative mounting angle ASP conforms to thestroke distance for each piston. The swash plate thereby urges thepistons back and forth as its edge rides in each piston's groove 1942.

The reed valves 1930 open and close in response to the stroke of therespective piston 1934 so that refrigerant is drawn (arrows 1928) infrom the shaft 1750 when pistons move in a downstroke (arrow 1950) andexpelled (arrows 1958) under compression into the ports 1920 when thepistons move in an upstroke (arrow 1952). Appropriate bearings 1960 andface seals 1962 prevent fluid loss through the housing at the interfacewith the connecting shaft 1750 and the drive shaft 1762. In this mannerthe flow (arrows 1780) of precompressed refrigerant into furthercompression in the first radial conduits 1780, condensation in the axialconduits 1784 and predetermined expansion in the second set of radial(return) conduits is maintained.

It should be clear that the operative principles used to construct theprecompressor are highly variable, and this embodiment can also beimplemented with a central hub that is free of a precompressor, and adiscrete, separate precompressor within the loop.

Note also, with reference to FIG. 18 that the region of counter-currentrefrigerant flow designated as ABCD is advantageously arranged totransfer heat in when certain types of refrigerant would benefit fromsuch heat-transfer. When using alternate refrigerants, a more adiabaticarrangement, with less or no heat transfer is desirable. In suchinstances, an insulating layer can be provided between the inner passage1842 and outer passages 1840.

By locating the drive sheave, inlet base and outlet base on one end ofthe device, it is contemplated in an alternate embodiment that theframework can be constructed in a cantilever manner. That is, thestructural support is primarily provided on one side of the device, andthe shaft is supported adjacent to the inlets and sheave.

As in other embodiments described herein, the size of conduits, passagesand other refrigerant-handling components is highly variable. Sizing isgenerally associated with desired BTU output and overall refrigerantcharge of the unit. Sizing of components can be optimized usingconventional fluid-dynamic and thermodynamic principles, as well asthrough experimentation, employing trial and error to determine optimumcomponent size.

It should be clear that the above-described ITCCE embodiments provide adurable, efficient and cost-effective solution to the need for a moreenergy efficient heat-transfer system. Theturbo-compressor-condenser-expander can be constructed from inexpensivecomponents and materials, exhibit a long working life, and significantlyreduce overall system component count.

The foregoing has been a detailed description of illustrativeembodiments of the invention. Various modifications and additions can bemade without departing from the spirit and scope of this invention. Eachof the various embodiments described above can be combined with otherdescribed embodiments in order to provide multiple features.Furthermore, while the foregoing describes a number of separateembodiments of the system and device of the present invention, what hasbeen described herein is merely illustrative of the application of theprinciples of the present invention. For example, the isothermalturbocompressor has been illustrated having blades surrounding andencasing the spokes entirely. However, the blades can comprise anystructure or orientation with respect to the spokes, wherein the bladesare in thermal communication with the channels or conduits associatedwith each of the spokes. Further, each spoke is depicted as including orsupporting one refrigerant channel/conduit, however any number ofchannels, conduits, pipes or tubes may be provided with respect to eachspoke. Likewise, not all spokes need support one or more conduits. Somespokes can act exclusively as structural supports for the fan/wheel,and/or as fan blades. The device is highly applicable to all airconditioning, refrigeration and/or heat-pumping systems. Also, thenumber of conduits, tubes or passages that are disposed with respect toeach spoke for the flow of refrigerant is highly variable, and the tubesor passages need not be of circular cross-section but may be varying insize and shape from tube to tube, or even along the same tube. Conduitsmay follow a straight path, a curved path, a sinuous path, or a path ofany other shape along the blades in which they are. The arrangement ofthe tubes is also variable. Moreover, the shape, size and materials ofthe turbocompressor and any associated housings, supports, brackets, andthe like are highly variable, and can be adapted to the system in whichthe turbocompressor is employed. In addition, the types of motor, power,control and fluid interconnections and systems associated with theturbocompressor are also highly variable and can be adapted to theparticular application in which theturbocompressor/turbo-compressor-condenser-expander is used.Accordingly, this description is meant to be taken only by way ofexample, and not to otherwise limit the scope of this invention.

What is claimed is:
 1. A turbo-compressor-condenser-expander assemblycomprising: a first plurality of spokes extending radially outwardlyfrom a first central hub to an outer perimeter, at least some of thefirst plurality of spokes each including a respective first radialconduit such that refrigerant is distributed evenly from the firstcentral hub to each of the respective first radial conduits associatedwith the at least some of the first plurality of spokes and subsequentlytransported to the outer perimeter and a radial blade in thermalcommunication with the first radial conduit that promotes heat exchangeradially; and a motor that rotates a central axis operatively connectedto the first central hub to thereby rotate the first plurality of spokesso that the refrigerant experiences centrifugal force to performcompression with respect to each first radial conduit.
 2. Theturbo-compressor-condenser-expander as set forth in claim 1 wherein thefirst central hub includes a precompression assembly.
 3. Theturbo-compressor-condenser-expander as set forth in claim 1 wherein theprecompression assembly comprises a housing having a piston assembly influid communication with each first radial conduit and wherein therefrigerant is directed into the piston assembly so as to beprecompressed by the piston assembly before entering each first radialconduit.
 4. The turbo-compressor-condenser-expander as set forth inclaim 1 further comprising a discrete precompressor unit operativelyconnected by a conduit to the first central huh.
 5. Theturbo-compressor-condenser-expander as set forth in claim 1 wherein thefirst central hub is operatively connected with a first rotating sealassembly that provides an axially stationary interface with an externalconduit of a refrigeration loop.
 6. Theturbo-compressor-condenser-expander as set forth in claim 5 wherein adrive axle is interconnected between the motor.
 7. Theturbo-compressor-condenser-expander as set forth in claim 1 wherein thefirst radial conduit defines at least one of (a) an internal spacewithin the radial blade, (b) at least one tube in thermal communicationwith the radial blade.
 8. The turbo-compressor-condenser-expander as setforth in claim 1 wherein at least some of the axial conduits eachinclude at least one of (a) an internal space within the axial blade,(b) a plurality of channels formed radially in a side-by-siderelationship along the axial blade, and (c) at least one tube in thermalcommunication with the axial blade.
 9. Theturbo-compressor-condenser-expander as set forth in claim 1 wherein theradial blade defines an approximately trapezoidal outline shape that isnarrower adjacent the first central hub and wider adjacent to the outerperimeter.
 10. The turbo-compressor-condenser-expander as set forth inclaim 1 wherein the radial blade and the axial blade each define across-section that is an airfoil having a narrow section at each ofopposing leading and trailing edges and a wider mid section, the midsection of the radial blade surrounding the first radial conduit and themid section of the axial blade surrounding the axial conduit.
 11. Asystem for performing compression and condensation of refrigerant inloop, the system comprising: a pre-compressor operatively connected to afirst drive interconnection, whereby the pre-compressor compresses therefrigerant; a turbo-compressor-condenser-expander defining a frameworkthat supports a plurality of radially directed first conduits thatextend from a from a first central hub to an outer perimeter radialblades each in thermal communication with at least some of the firstconduits; and a second drive interconnection that rotates a central axleoperatively connected with the first central hub to impart centrifugalforce to the refrigerant located in the first conduits, to cause therefrigerant to undergo compression as it travels through the firstconduits and to cause the refrigerant to be distributed evenly from thefirst central hub to each of the first conduits.
 12. The system as setforth in claim 11 wherein the first drive interconnection and the seconddrive interconnection are each operatively connected to a common motor.13. The system as set forth in claim 11 wherein the framework isconstructed and arranged to allow free airflow around the radial bladesand the axial blades.
 14. The turbo-compressor-condenser-expander as setforth in claim 6 further comprising an outer sleeve that defines a gapbetween the drive axle and the sleeve to allow the refrigerant to passtherebetween.
 15. The turbo-compressor-condenser-expander as set forthin claim 1, at least some of the first plurality of spokes each furthercomprising a plurality of radial conduits formed radially in aside-by-side relationship along the radial blade.
 16. Theturbo-compressor-condenser-expander as set forth in claim 1, furthercomprising a second plurality of spokes extending radially outwardlyfrom a second central hub located at an axial spacing from the firstcentral hub, at least some of the second plurality of spokes eachincluding a second radial conduit that transports refrigerant from theouter perimeter to the second central hub.
 17. Theturbo-compressor-condenser-expander as set forth in claim 16, furthercomprising a plurality of axial conduits extending axially at the outerperimeter between the first plurality of spokes and the second pluralityof spokes, and each interconnecting the first radial conduit and thesecond radial conduit, respectively, to direct refrigerant therebetween,at least some of the plurality of axial conduits each including an axialblade in thermal communication with the axial conduit that promotes heatexchange.
 18. The turbo-compressor-condenser-expander as set forth inclaim 16, further comprising axial blades each in thermal communicationwith at least some of the axial conduits.
 19. Theturbo-compressor-condenser-expander as set forth in claim 3, wherein thecentral axis defines a hollow shaft that directs the refrigerant from aninlet adjacent the second central hub into the piston assembly so as tobe precompressed by the piston assembly before entering each firstradial conduit.
 20. The turbo-compressor-condenser-expander as set forthin claim 19 wherein the inlet adjacent to the second central hub islocated on a non-rotating inlet base of a rotating fluid union, andwherein the rotating fluid union includes a non-rotating outlet base,axially separated from the inlet base, the outlet base being in fluidcommunication with passages that surround a central passage incommunication with the inlet, the passages being in fluid communicationwith each second radial conduit.